JPS6294415A - Cooler for vehicle - Google Patents
Cooler for vehicleInfo
- Publication number
- JPS6294415A JPS6294415A JP60234823A JP23482385A JPS6294415A JP S6294415 A JPS6294415 A JP S6294415A JP 60234823 A JP60234823 A JP 60234823A JP 23482385 A JP23482385 A JP 23482385A JP S6294415 A JPS6294415 A JP S6294415A
- Authority
- JP
- Japan
- Prior art keywords
- refrigeration cycle
- refrigeration
- auxiliary
- condenser
- cycles
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
- B60H1/00—Heating, cooling or ventilating [HVAC] devices
- B60H1/32—Cooling devices
- B60H1/3204—Cooling devices using compression
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- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
本発明は、バスなどの大型車両用の冷房装置に係り、特
に冷凍サイクルを２系統具備した車両用冷房装置に関す
る。DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a cooling system for a large vehicle such as a bus, and more particularly to a cooling system for a vehicle equipped with two refrigeration cycles.
〔従来の技術〕
車両用冷房装置は、盛夏の日中には大きな冷房能力を必
要とし、それ以外の時には比較的小さな冷房能力で済む
。そこで冷凍力イクルを２系統具備し、盛夏の日中には
両系統を使用し、それ以外のとき一系統のみを使用し省
エネを図る冷房装置が知られている。[Prior Art] A vehicle cooling system requires a large cooling capacity during the daytime in midsummer, and requires a relatively small cooling capacity at other times. Therefore, a cooling system is known that is equipped with two systems of refrigeration power cycles and uses both systems during the daytime in midsummer, and uses only one system at other times to save energy.
第４図は、このような２系統の冷凍サイクルを具備する
車両用冷房装置の一例を示したもので、フレーム１に取
付けられたサブエンジン２は２系統の冷凍サイクルを駆
動する。第１の冷凍サイクルはコンプレッサ３Ａ、コン
デンサ４Ａ、膨張弁５Ａ、エバポレータ６Ａなどから成
り、第２の冷凍サイクルも同様にコンプレブザ３Ｂ、コ
ンデンサ４Ｂ、膨張弁５Ｂ、エバポレータ６Ｂなどから
構成されている。コンプレッサ３Ａ、３Ｂはそれぞれ図
示を省略した電磁クラッチを介してサブエンジン２によ
り駆動され、またコンデンサ４Ａ１４Ｂはザブエンジン
２によって駆動される送風フアン７の前方に順次配置さ
れている。即ち、送風路中に直列に配置されている。室
内空気循環用送風機８は駆動系９を介してサブエンジン
２によって駆動される。この送Ｊ！ｌｌ！１８の送風に
対して一対のエバポレータ６Ａ、６Ｂは直列に配置され
ている。FIG. 4 shows an example of a vehicle cooling system equipped with such two systems of refrigeration cycles, and the sub-engine 2 attached to the frame 1 drives the two systems of refrigeration cycles. The first refrigeration cycle is composed of a compressor 3A, a condenser 4A, an expansion valve 5A, an evaporator 6A, etc., and the second refrigeration cycle is similarly composed of a compressor 3B, a condenser 4B, an expansion valve 5B, an evaporator 6B, etc. The compressors 3A and 3B are each driven by the sub-engine 2 via electromagnetic clutches (not shown), and the capacitors 4A14B are sequentially arranged in front of the blower fan 7 driven by the sub-engine 2. That is, they are arranged in series in the air passage. The indoor air circulation blower 8 is driven by the sub-engine 2 via a drive system 9. This sending J! ll! A pair of evaporators 6A and 6B are arranged in series for 18 air blowers.
第５図は別の従来の車両用冷房装置を示したもので、一
対のコンプレッサ４Ａ、４Ｂがそれぞれ送風ファン７に
対向するように互いに並置され、■バボレータ６Ａ、６
Ｂも同様に並置されている。FIG. 5 shows another conventional vehicle cooling system, in which a pair of compressors 4A and 4B are arranged in parallel to each other so as to face a blower fan 7.
B is also juxtaposed in the same way.
しかしながら、第４図の冷房装置では、コンデンサ４Ｂ
はコンデンサ４Ａを冷却し温度玉貸した空気で冷却され
るので、この後流のコンデンサ４Ｂの放熱量は上流のコ
ンデンサ４Ａに比べて相当に低下し、このため、第２冷
凍サイクルの冷凍サイクルの冷房能力が第１冷凍サイク
ルに比べて低下してしまう問題点がある。However, in the cooling system shown in FIG. 4, the capacitor 4B
is cooled by the air that cools the condenser 4A and lends a temperature ball, so the amount of heat dissipated from the downstream condenser 4B is considerably lower than that of the upstream condenser 4A. There is a problem that the cooling capacity is lower than that of the first refrigeration cycle.
他方、第５図の冷房装置では、コンデンサ４Ａ。On the other hand, in the cooling device of FIG. 5, the condenser 4A.
４Ｂが並置されているので、両冷凍サイクルの冷房能力
は互いに等しいが、しかしながら一方の冷凍サイクルの
みを使用する場合送風ファン７による送ｙｉ量の半分し
か有効に使用できず、エネルギの無駄が大きいといった
欠点がある。4B are placed side by side, the cooling capacity of both refrigeration cycles is equal to each other. However, if only one refrigeration cycle is used, only half of the amount yi sent by the blower fan 7 can be effectively used, resulting in a large waste of energy. There are drawbacks such as:
そこで、本発明の目的は、２系統の冷凍サイクルの冷房
能力を等しくできると共に、一方の冷凍サイクルのみを
運転した場合にもコンデンサ冷却用送風を無駄なく利用
することができる車両用冷房装置を提供することにある
。SUMMARY OF THE INVENTION Accordingly, an object of the present invention is to provide a vehicle cooling system that can equalize the cooling capacity of two refrigeration cycles and that can utilize condenser cooling air without waste even when only one refrigeration cycle is operated. It's about doing.
この目的を達成するための本発明の構成を実施例に対応
する第１図〜第３図を用いて説明する。The structure of the present invention for achieving this object will be explained using FIGS. 1 to 3 corresponding to embodiments.
第１および第２冷凍サイクルの各々は互いに直列に接続
されたコンデンサ１０Ａ、ＩＯＢと冷媒補助冷却器１１
Ａ、１１Ｂ又は１５Ａ、１５Ｂとを有し、第１．第２冷
凍サイクルのコンデンサ１゜Ａ、１０Ｂは、それぞれ送
風ファン７に対向するように並置され、第１．第２冷凍
サイクルの補助冷却器１１Ａ、１１Ｂ又は１５Ａ、１５
Ｂは第１冷凍サイクルの補助冷却器１１Ａ又は１５Ａが
第２冷凍サイクルのコンデンサＩＯＢに対向し第２冷凍
サイクルの補助冷却器１１Ｂ又は１５Ｂが第１冷凍サイ
クルのコンデンサ１０Ａに対向するように、並置されて
いる。Each of the first and second refrigeration cycles includes a capacitor 10A, an IOB, and a refrigerant auxiliary cooler 11 connected in series with each other.
A, 11B or 15A, 15B, and the first. The condensers 1°A and 10B of the second refrigeration cycle are arranged side by side so as to face the blower fan 7, respectively. Auxiliary cooler 11A, 11B or 15A, 15 of the second refrigeration cycle
B is arranged in parallel so that the auxiliary cooler 11A or 15A of the first refrigeration cycle faces the condenser IOB of the second refrigeration cycle, and the auxiliary cooler 11B or 15B of the second refrigeration cycle faces the condenser 10A of the first refrigeration cycle. has been done.
（作用）
本発明は上述の構成により、両冷凍サイクルの運転時に
は第１冷凍サイクルのコンデンサ１０Ａと補助冷却器１
１Ａ１又は１５Ａ及び、第２冷凍サイクルのコンデンサ
１１Ａと補助冷却器１１Ｂ又は１５Ｂが送風ファンの送
風に対して同一冷却条件となるため両冷凍サイクルの冷
房能力を等しくでき、また、一方の冷凍サイクルのみの
運転時にはその冷凍サイクルのコンデンサと補助冷却器
とが送風を無駄なく利用することができる。(Function) With the above-described configuration, the present invention has the condenser 10A of the first refrigeration cycle and the auxiliary cooler 1 when both refrigeration cycles are in operation.
1A1 or 15A, the condenser 11A of the second refrigeration cycle, and the auxiliary cooler 11B or 15B have the same cooling conditions for the air from the blower fan, so the cooling capacity of both refrigeration cycles can be made equal, and only one refrigeration cycle can be used. During operation, the condenser and auxiliary cooler of the refrigeration cycle can utilize the air without wasting it.
（実施例）
以下に本発明による車両用冷房装置の一実施例を説明す
る。なお、第４図と第５図と同部分には同一符号が付さ
れている。(Example) An example of a vehicle cooling device according to the present invention will be described below. Note that the same parts as in FIGS. 4 and 5 are given the same reference numerals.
第１図において、フレーム１の中央部にサブエンジン２
が搭載され、このザブエンジン２は２系統の冷凍サイク
ルを駆動する。第１の冷凍サイクルは、コンプレッサ３
Ａと、主コンデンサ１０Ａと、補助コンデンサ１１Ａと
、膨張弁５Ａと、■バポレータ６Ａなどから成り、同様
に第２の冷凍サイクルもコンプレッサ３Ｂと、主コンデ
ンサ１０Ｂと、補助コンデンサ１１Ｂと、膨張弁５Ｂと
、エバポレータ６Ｂなどから構成されている。In Figure 1, the sub-engine 2 is located in the center of the frame 1.
This subengine 2 drives two refrigeration cycles. The first refrigeration cycle consists of compressor 3
A, a main condenser 10A, an auxiliary condenser 11A, an expansion valve 5A, and a vaporator 6A.Similarly, the second refrigeration cycle also consists of a compressor 3B, a main condenser 10B, an auxiliary condenser 11B, and an expansion valve 5B. and an evaporator 6B.
コンプレッサ３Ａ、３Ｂはそれぞれ図示を省略された電
磁クラッチを介してサブエンジン２により駆動される。The compressors 3A and 3B are each driven by the sub-engine 2 via electromagnetic clutches (not shown).
各冷凍サイクルの主コンデンサ１０Ａ、ＩＯＢと補助コ
ンデンサ１１Ａ、ＩＩＢは、主コンデンサ１０Ａ、１０
Ｂで冷却された冷媒を補助コンデンサ１１Ａ、１１Ｂで
更に過冷却するように、互いに直列に接続されている。The main capacitors 10A, IOB and auxiliary capacitors 11A, IIB of each refrigeration cycle are the main capacitors 10A, 10
They are connected in series to each other so that the refrigerant cooled by B is further subcooled by auxiliary capacitors 11A and 11B.
また、各コンデンサ１０Ａ、１０Ｂ、１１Ａ、１１Ｂの
配置関係は次のように定められている。すなわち、第１
．第２冷凍サイクルの主コンデンサ１０Ａ、１０Ｂは、
ザブエンジン２により駆動される送風ファン７に夫々対
向するように互い。に並置され、第１．第２冷凍サイク
ルの補助コンデンサ１１Ａ、１１Ｂは、第１冷凍サイク
ルの補助コンデンナ１１Ａが第２冷凍サイクルの主コン
デンサ１０Ｂと対向し、第２冷凍サイクルの補助コンデ
ンサ１１Ｂが第１冷凍サイクルの主コンデンサ１０Ａと
対向するように、互いに並置されている。Moreover, the arrangement relationship of each capacitor 10A, 10B, 11A, and 11B is determined as follows. That is, the first
．． The main condensers 10A and 10B of the second refrigeration cycle are
and each other so as to face the blower fans 7 driven by the subengine 2, respectively. juxtaposed to the 1st. The auxiliary capacitors 11A and 11B of the second refrigeration cycle are such that the auxiliary condenser 11A of the first refrigeration cycle faces the main capacitor 10B of the second refrigeration cycle, and the auxiliary capacitor 11B of the second refrigeration cycle faces the main capacitor 10A of the first refrigeration cycle. They are juxtaposed to each other so that they are facing each other.
室内空気循環用送風４ｊｌＢは駆動系９を介してザブエ
ンジン２によって駆動される。The indoor air circulation blower 4jlB is driven by the subengine 2 via a drive system 9.
次に上述した本発明による装置の作用を説明する。Next, the operation of the apparatus according to the present invention described above will be explained.
盛夏の日中のように大きな冷房能力が必要な場合には、
両コンプレッサ３Ａ、３Ｂが共にサブエンジン２により
駆動される。第１冷凍サイクルのコンプレッサ３Ａから
吐出された冷媒は主コンデンサ１０Ａに流入し凝縮され
、ここを出た高圧冷媒は補助コンデンサ１１Ａに流入し
て凝縮を完了し、図示を省略されたリキッドタンクを経
て膨張弁５Ａで膨張される。この膨張された冷媒は、■
バポレータ６Ａにおいて蒸発して、室内空気循環用送風
機８により吸込まれた室内空気を冷却し、この後再びコ
ンプレッサ３Ａに戻る。第２冷凍サイクルについても第
１冷凍サイクルの作用と同様である。When large cooling capacity is required, such as during midsummer days,
Both compressors 3A and 3B are driven by the sub-engine 2. The refrigerant discharged from the compressor 3A of the first refrigeration cycle flows into the main condenser 10A and is condensed, and the high-pressure refrigerant that exits here flows into the auxiliary condenser 11A to complete condensation, and then passes through a liquid tank (not shown). It is expanded by the expansion valve 5A. This expanded refrigerant is
The indoor air is evaporated in the vaporizer 6A, cools the indoor air sucked in by the indoor air circulation blower 8, and then returns to the compressor 3A again. The second refrigeration cycle also operates in the same way as the first refrigeration cycle.
このように第１．第２冷凍サイクルの両方が使用された
場合、第１冷凍サイクルの主及び補助コンデンサ１０Ａ
、１１Ａは第２冷凍サイクルの主及び補助コンデンサ１
０Ｂ、１１Ｂと全く同一条件下で、送風を受けるので、
両冷凍サイクルの冷房能力は等しくなる。In this way, the first. If both second refrigeration cycles are used, the first refrigeration cycle main and auxiliary capacitors 10A
, 11A is the main and auxiliary condenser 1 of the second refrigeration cycle.
Since it receives ventilation under exactly the same conditions as 0B and 11B,
The cooling capacity of both refrigeration cycles will be equal.
また、一方の冷凍サイクル、例えば第１冷凍サイクルの
みを運転する場合には送風ファン７による全送風を主コ
ンデンサ１０Ａと補助コンデンサ１１Ａとで受けるので
、送風を無駄なく利用することができる。Further, when only one refrigeration cycle, for example the first refrigeration cycle, is operated, all the air blown by the blower fan 7 is received by the main condenser 10A and the auxiliary condenser 11A, so that the air blown can be used without waste.
第２図は、第１．第２冷凍サイクルの主コンデンサ１０
Ａ、１０Ｂ及び補助コンデンサ１１Ａ。Figure 2 shows the 1. Main condenser 10 of the second refrigeration cycle
A, 10B and auxiliary capacitor 11A.
１１Ｂとの具体的構成例を示したもので、一対の主コン
デンサ１０Ａと１０Ｂは一体化され、熱交換器１２とし
て構成され、一対の補助コンデンサ１１Ａと１１Ｂも一
体化され補助熱交換器１３として構成されている。11B, a pair of main capacitors 10A and 10B are integrated to form a heat exchanger 12, and a pair of auxiliary capacitors 11A and 11B are also integrated to form an auxiliary heat exchanger 13. It is configured.
第３図は本発明の変形例を示したもので、第１゜第２冷
凍サイクルのコンデンサ１０△、１０Ｂで凝縮した冷媒
はそれぞれリキッドタンク１４Ａ。FIG. 3 shows a modification of the present invention, in which the refrigerant condensed in the condensers 10Δ and 10B of the first and second refrigeration cycles are stored in liquid tanks 14A, respectively.
１４Ｂに流入し、このリキッドタンク１４Ａ。14B, and this liquid tank 14A.
１４Ｂからの液冷媒は、サブクーラ１５Ａ、１５Ｂで再
び過冷却されてそれぞれ熱膨張弁５Ａ、５Ｂに送られる
。第１．第２冷凍サイクルのサブクーラ１５Ａ、１５Ｂ
はそれぞれ第１図の補助コンデンサ１１Ａ、ＩＩＢと同
様に、］コンデンサ。The liquid refrigerant from 14B is subcooled again in subcoolers 15A and 15B and sent to thermal expansion valves 5A and 5B, respectively. 1st. Subcoolers 15A and 15B of the second refrigeration cycle
are ] capacitors, similar to the auxiliary capacitors 11A and IIB in FIG. 1, respectively.
Ｂ、１０Ａに対向するように、互いに並置されている。B and 10A are arranged in parallel to each other so as to face each other.
また、本例では第１．第２冷凍サイクルのエバポレータ
は、それぞれ主エバポレータ６Ａ。In addition, in this example, the first. The evaporators of the second refrigeration cycle are the main evaporators 6A.
６Ｂと、この主エバポレータからの冷媒をさらに気化さ
せる補助エバポレータ１６Ａ、１６Ｂとから構成されて
いる。第１．第２冷凍ナイクルの主エバポレータ６Ａ、
６Ｂは互いに並置され、補助エバポレータ１６Ａは、主
エバポレータ６Ｂに、補助エバポレータ１６Ｂは主エバ
ポレータ６Ａに対向するように配置されている。このよ
うに第１冷凍サイクルの主および補助エバポレータ６Ａ
。6B, and auxiliary evaporators 16A and 16B that further vaporize the refrigerant from the main evaporator. 1st. The main evaporator 6A of the second frozen Nicle,
6B are arranged in parallel with each other, and the auxiliary evaporator 16A is arranged to face the main evaporator 6B, and the auxiliary evaporator 16B is arranged to face the main evaporator 6A. In this way, the main and auxiliary evaporators 6A of the first refrigeration cycle
.
１６Ａと第２冷凍サイクルの主、および補助エバポレー
タ６Ｂ、１６Ｂとが、互いにクロスするように配置され
ているので、両冷凍サイクルのエバポレータを送風機８
による送風に対して互いに同一条件とすることができる
。16A and the main and auxiliary evaporators 6B, 16B of the second refrigeration cycle are arranged so as to cross each other, so the evaporators of both refrigeration cycles are connected to the blower 8.
The conditions for air blowing can be set to be the same.
以上の説明から明らかなように本願の第１発明によると
、第１．第２冷凍サイクルのコンデンサをそれぞれ送風
ファンに対向するように互いに並置すると共に、第１．
第２冷凍サイクルの補助コンデンサやサブクーラのよう
な冷媒補助冷却器を第１冷凍サイクルの冷媒補助冷却器
が第２冷凍サイクルのコンデンサに対向し、第２冷凍サ
イクルの冷媒補助冷却器が第１冷凍サイクルのコンデン
サに対向するように並置されているため、第１゜第２冷
凍サイクルのコンデンサと冷媒補助冷却器が同一冷却条
件下に直かれ両サイクルの冷房能力を等しくでき、かつ
一方の冷凍サイクルのみを運転する場合にもコンデンサ
と冷媒補助冷却器にょり送風の全体を無駄なく利用する
ことができる。As is clear from the above description, according to the first invention of the present application, the first aspect of the invention is as follows. The condensers of the second refrigeration cycle are arranged in parallel to each other so as to face the blower fans, and the condensers of the second refrigeration cycle are arranged in parallel with each other so as to face the blower fans.
A refrigerant auxiliary cooler such as an auxiliary condenser or a subcooler in the second refrigeration cycle is connected to the refrigerant auxiliary cooler in the first refrigeration cycle, which faces the condenser in the second refrigeration cycle, and a refrigerant auxiliary cooler in the second refrigeration cycle in the first refrigeration cycle. Since the condensers of the first and second refrigeration cycles are placed side by side to face each other, the condensers and refrigerant auxiliary coolers of the first and second refrigeration cycles are placed under the same cooling conditions, making it possible to equalize the cooling capacity of both cycles. Even when operating only the condenser and refrigerant auxiliary cooler, the entire air supply can be used without waste.
さらに過冷却部分が補助冷却器としてコンデンサから分
離されているので、凝縮中の冷媒管に付設された放熱フ
ィンからの熱伝導が無く補助冷却器の過冷却効果を向上
できる。Further, since the supercooled portion is separated from the condenser as an auxiliary cooler, there is no heat conduction from the radiation fins attached to the refrigerant pipe during condensation, and the supercooling effect of the auxiliary cooler can be improved.
また、本願の第２発明によると第１．第２冷凍サイクル
のコンデンυと補助冷却器とのクロス配置に加えて主エ
バポレータと補助エバポレータも互いにクロス配置され
ているため、第１発明の効果に加えて第１．第２冷凍サ
イクルの冷媒蒸発量を等しくできる。さらに一方の冷凍
サイクルのみを運転した場合にもこのサイクルの主エバ
ポレータと補助エバポレータとが室内循環空気を無駄な
く受けるので、冷房効果が向上し、かつ低温時の霜付現
象の発生を抑制できる。According to the second invention of the present application, the first invention. In addition to the cross arrangement of the condenser υ and the auxiliary cooler of the second refrigeration cycle, the main evaporator and the auxiliary evaporator are also arranged in a cross relation with each other, so that in addition to the effects of the first invention, the first. The amount of refrigerant evaporated in the second refrigeration cycle can be made equal. Furthermore, even when only one of the refrigeration cycles is operated, the main evaporator and auxiliary evaporator of this cycle receive indoor circulating air without waste, improving the cooling effect and suppressing the occurrence of frosting at low temperatures.
第１図は本発明による車両用冷房装置の一実施例を示し
た概略図、第２図は第１図の主コンデンサと補助コンデ
ンサの貝体的構成例を示した斜視図、第３図は本発明の
第２実施例を示した概略図、第４図と第５図はそれぞれ
従来の車両用冷房装置を示した概略図である。
７・・・送風フッ７ン、１０Ａ・・・第１冷凍サイクル
のコンデンサ、１０Ｂ・・・第２冷凍サイクルの］ンデ
ンザ、１１Ａ・・・第１冷凍サイクルの補助コンデンサ
、１１Ｂ・・・第２冷凍サイクルの補助コンデンサ、１
５Ａ・・・第１冷凍サイクルのサブクーラ、１５Ｂ・・
・第２冷凍サイクルのサブクーラ。
出願人代理人 佐 藤 −雄
午 ｌ 図
蔓 ２ 図FIG. 1 is a schematic diagram showing an embodiment of a vehicle cooling system according to the present invention, FIG. 2 is a perspective view showing an example of a shell-like structure of the main capacitor and auxiliary capacitor shown in FIG. 1, and FIG. A schematic diagram showing a second embodiment of the present invention, and FIGS. 4 and 5 are schematic diagrams showing a conventional vehicle cooling system, respectively. 7...Air blower 7, 10A...Condenser of the first refrigeration cycle, 10B...Ndenza of the second refrigeration cycle, 11A...Auxiliary condenser of the first refrigeration cycle, 11B...Second Refrigeration cycle auxiliary condenser, 1
5A...Subcooler of the first refrigeration cycle, 15B...
・Subcooler of the second refrigeration cycle. Applicant's agent: Sato-Yugo l Figure 2
Claims (6)
置において、上記第１および第２冷凍サイクルの各々は
互いに直列に接続されたコンデンサと冷媒補助冷却器と
を有し、上記第１，第２冷凍サイクルのコンデンサはそ
れぞれ送風ファンに対向するように並置され、上記第１
，第２冷凍サイクルの冷媒補助冷却器は、第１冷凍サイ
クルの冷媒補助冷却器が上記第２冷凍サイクルのコンデ
ンサに対向し上記第２冷凍サイクルの冷媒補助冷却器が
上記第１冷凍サイクルのコンデンサに対向するように、
並置されていることを特徴とする車両用冷房装置。1. In a vehicle cooling system having first and second refrigeration cycles, each of the first and second refrigeration cycles has a condenser and a refrigerant auxiliary cooler connected in series, and the first and second refrigeration cycles each include a condenser and a refrigerant auxiliary cooler, The cycle capacitors are arranged side by side to face the blower fan, and
, the refrigerant auxiliary cooler of the second refrigeration cycle is such that the refrigerant auxiliary cooler of the first refrigeration cycle faces the condenser of the second refrigeration cycle, and the refrigerant auxiliary cooler of the second refrigeration cycle faces the condenser of the first refrigeration cycle. As if facing the
A vehicle cooling device characterized in that they are arranged side by side.
サから上記冷媒補助冷却器に送られることを特徴とする
特許請求の範囲第１項記載の車両用冷房装置。2. 2. The vehicle cooling system according to claim 1, wherein the refrigerants of the first and second refrigeration cycles are sent from the condenser to the refrigerant auxiliary cooler.
いに一体に構成され、上記第１，第２冷凍サイクルのコ
ンデンサも互いに一体に構成されていることを特徴とす
る特許請求の範囲第１項又は第２項に記載の車両用冷房
装置。3. Claim 1, wherein the refrigerant auxiliary coolers of the first and second refrigeration cycles are integrally constructed, and the condensers of the first and second refrigeration cycles are also integrally constructed. Or the vehicle cooling device according to item 2.
置において、上記第１および第２冷凍サイクルの各々は
互いに直列に接続されたコンデンサと冷媒補助冷却器、
および互いに直列な主エバポレータと補助エバポレータ
とを有し、上記第１，第２冷凍サイクルのコンデンサは
それぞれ送風ファンに対向するように並置され、上記第
１，第２冷凍サイクルの冷媒補助冷却器は、第１冷凍サ
イクルの冷媒補助冷却器が上記第２冷凍サイクルのコン
デンサに対向、上記第２冷凍サイクルの冷媒補助冷却器
が上記第１冷凍サイクルのコンデンサに対向するように
、並置され、また上記第１，第２冷凍サイクルの主エバ
ポレータは互いに並置され、上記第１，第２冷凍サイク
ルの補助エバポレータは、第１冷凍サイクルの補助エバ
ポレータが上記第２冷凍サイクルの主エバポレータに対
向し、上記第２冷凍サイクルの補助エバポレータが上記
第１冷凍サイクルの主エバポレータに対向するように並
置されていることを特徴とする車両用冷房装置。4. In a vehicle cooling system having first and second refrigeration cycles, each of the first and second refrigeration cycles includes a condenser and a refrigerant auxiliary cooler connected in series with each other;
and a main evaporator and an auxiliary evaporator that are in series with each other, the condensers of the first and second refrigeration cycles are arranged in parallel to face the blower fans, and the refrigerant auxiliary coolers of the first and second refrigeration cycles are , the refrigerant auxiliary cooler of the first refrigeration cycle faces the condenser of the second refrigeration cycle, and the refrigerant auxiliary cooler of the second refrigeration cycle faces the condenser of the first refrigeration cycle, and the The main evaporators of the first and second refrigeration cycles are arranged in parallel with each other, and the auxiliary evaporators of the first and second refrigeration cycles are arranged such that the auxiliary evaporator of the first refrigeration cycle faces the main evaporator of the second refrigeration cycle, and the auxiliary evaporators of the first and second refrigeration cycles are arranged in parallel with each other. A vehicle cooling system characterized in that the auxiliary evaporators of two refrigeration cycles are arranged in parallel to face the main evaporator of the first refrigeration cycle.
ータから上記冷媒補助冷却器に送られることを特徴とす
る特許請求の範囲第１項に記載の車両用冷房装置。5. 2. The vehicle cooling system according to claim 1, wherein the refrigerants of the first and second refrigeration cycles are sent from the evaporator to the refrigerant auxiliary cooler.
いに一体に構成され、上記第１，第２冷凍サイクルのエ
バポレータも互いに一体に構成されていることを特徴と
する特許請求の範囲第１項又は第２項に記載の車両用冷
房装置。6. Claim 1, characterized in that the refrigerant auxiliary coolers of the first and second refrigeration cycles are constructed integrally with each other, and the evaporators of the first and second refrigeration cycles are also constructed integrally with each other. Or the vehicle cooling device according to item 2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60234823A JPH0798450B2 (en) | 1985-10-21 | 1985-10-21 | Vehicle cooling system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP60234823A JPH0798450B2 (en) | 1985-10-21 | 1985-10-21 | Vehicle cooling system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6294415A true JPS6294415A (en) | 1987-04-30 |
| JPH0798450B2 JPH0798450B2 (en) | 1995-10-25 |
Family
ID=16976940
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP60234823A Expired - Lifetime JPH0798450B2 (en) | 1985-10-21 | 1985-10-21 | Vehicle cooling system |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0798450B2 (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001194014A (en) * | 2000-01-13 | 2001-07-17 | Mitsubishi Electric Corp | Freezing cycle apparatus and freezing refrigerator |
| KR20020025507A (en) * | 2000-09-29 | 2002-04-04 | 황한규 | Heat exchanger with dual evaporator |
| JP2007178072A (en) * | 2005-12-28 | 2007-07-12 | Sanden Corp | Air conditioner for vehicle |
| WO2019181627A1 (en) * | 2018-03-23 | 2019-09-26 | サンデン・オートモーティブクライメイトシステム株式会社 | Air conditioning device for vehicle |
-
1985
- 1985-10-21 JP JP60234823A patent/JPH0798450B2/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2001194014A (en) * | 2000-01-13 | 2001-07-17 | Mitsubishi Electric Corp | Freezing cycle apparatus and freezing refrigerator |
| KR20020025507A (en) * | 2000-09-29 | 2002-04-04 | 황한규 | Heat exchanger with dual evaporator |
| JP2007178072A (en) * | 2005-12-28 | 2007-07-12 | Sanden Corp | Air conditioner for vehicle |
| WO2019181627A1 (en) * | 2018-03-23 | 2019-09-26 | サンデン・オートモーティブクライメイトシステム株式会社 | Air conditioning device for vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH0798450B2 (en) | 1995-10-25 |
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